Heat exchanger comprising an integrated supply and discharge

ABSTRACT

A heat exchanger, with a core region having a plurality of tube bundles through which a fluid flows in series is provided with at least one specially designed header composed of two half shells. The specially designed header deflects the fluid stream between two successive tube bundles in opposite directions, with the supply and discharge of the fluid to and from the core region through the header. The resulting heat exchanger is structurally simple, having a minimum number of components to be mounted.

This application is a national phase application of Internationalapplication PCT/EP2004/009111, filed Aug. 13, 2004 and claims thepriority of German application No. 103 39 072.3, filed Aug. 26, 2003,the disclosure of which are expressly incorporated by reference herein.

BACKGROUND AND SUMMARY OF THE INVENTION

The invention relates to a heat exchanger for a fluid.

Heat exchangers are used, for example, in the air conditioning systemsof motor vehicles, in which, via the multiplicity of tubes and largesurface resulting from these, heat transmission between the fluidcirculating in the tubes and the outside air is carried out. The variousapplications may involve both changes in temperature of the fluid andchanges in heat due to phase transition of the fluid.

Such a heat exchanger is known, for example, from DE 198 30 329 A1. Theheat exchanger described in this publication is a coolant or refrigerantcondenser with a core region having a multiplicity of tubes which extendhorizontally and are arranged parallel to one a meandering manner, thedeflection of the fluid when it emerges from one of the tubes or tubebundles and when it reenters the next tube or tube bundle in theopposite direction taking place in headers arranged on both end faces ofthe tubes and open with respect to these. The inflow and outflow of thecoolant or refrigerant into and out of the heat exchanger take place viaa connecting block which is connected via pipelines to the first tubewhere the fluid enters the heat exchanger and to the last tube when thefluid emerges from the heat exchanger.

An object of the invention is to provide a heat exchanger which isstructurally simple and having a minimum number of components to bemounted on the heat exchanger.

To achieve this object, in a generic heat exchanger, there is provided aheat exchanger in which at least one header has in the longitudinaldirection a partition which subdivides the header into a first regionopen to the tubes and connecting these and a second region which is abypass with respect to the tube bundles.

With the at least one header being divided, this gives rise not only tothe region in which the control and deflection of the fluid streammeandering through the serial tube bundles take place, but also to asecond region which forms a bypass with respect to the tube bundles.This arrangement makes it possible to control the entire fluid streamwithin the heat exchanger solely by the tubes of the core region and theheaders in each case arranged on the end faces of the tubes. Since theheader or headers assumes or assume the function of supplies anddischarges with respect to the core region of the heat exchanger,further functional components in this respect are unnecessary.

In an advantageous development, a block having the supply and dischargeswith respect to the heat exchanger is arranged at one end of the header.Via this block, the fluid is supplied to the heat exchanger and, afterbeing routed to the individual tubes or tube bundles from thecorresponding regions in the header, is discharged from the heatexchanger again.

Also advantageously, the longitudinal partition of the header has atleast two passage orifices through which the fluid can be conducted fromthe conducting region of the header through the passage orifices and viathe deflection region of the header and be returned in the oppositedirection. Depending on the choice of position of the passage orifices,fluid exchange between the conducting region of the header and the tubescan take place at a largely freely selectable point over the length ofthe header, with the result that the flow path of fluid through the tubebundles can also be influenced.

In this case, a connection to a tube bundle can be formed by at leastone first of the passage orifices in the longitudinal partition and aconnection to the junctions of the block can be formed by at least onesecond of the passage orifices. That is to say, the fluid stream can berouted from the block into the deflection region of the header, thenconducted through the tube system in a meandering manner and be led backto the block via the conducting region of the header. The fluid streamcan also be routed in the same way in the opposite direction.

In this case, it is beneficial to arrange the block having the suppliesand discharges fixedly on the header, so that the entire heat exchangercan be mounted in one piece without further additional components.

It is expedient, further, for the header to be composed of an open halfshell and of a closed half shell which can be connected fixedly in asimple way.

In a first alternative design, the second region is open over the lengthof the header, so that the fluid stream can be conducted over the entirelength of the header between the block and, selectively, the startingpoint of the end point of the fluid stream in the heat exchanger.

In the second alternative embodiment, that region of the header whichfaces away from the tubes is subdivided into two separate regions, withthe result that at least two independent fluid streams can be routed inthe region. By means of this configuration, there is the possibility ofintroducing and discharging the fluid stream into and out of the systemof tubes or tube bundles at two different points and of being able toroute the fluid streams resulting from these in the second region of theheader completely independently of one another.

In an advantageous design of the second alternative, the region issubdivided into two ducts arranged in parallel. Thus, in a simpleproduction process, a header can be produced, by means of which aplurality of introductions and discharges of the fluid stream into andout of the conducting region of the header can be carried out at afreely selectable point, without the inflow and the return flow of thefluid stream from the block being impaired.

In an expedient development, in this case, the closed half shell isdesigned in a structurally simple way as a double chamber.

In the invention, taken as a whole, the headers are advantageouslydesigned to be pushed into a guide rail for holding the heat exchanger.One of the criteria for the advantageous configuration of the heatexchanger is to limit this to a minimum number of necessary componentsand to fulfill all the functions by means of these necessary components.

In an expedient design of the invention, the heat exchanger is an airconditioning condenser, in which a coolant or refrigerant is transferredfrom a gaseous phase into a liquid phase, with heat being dischargedinto the ambient air.

Alternatively, the heat exchanger may also be designed as a gas cooler.

In the case of an air conditioning condenser, it is particularlyadvantageous to design the last pass through one of the tubes or tubebundles as a supercooling stage, in each case, in the second alternativedesign of the header, the supercooling stage does not have to bearranged on one of the end pieces of the header, but may be arrangedfreely over the entire length of the header.

Other objects, advantages and novel features of the present inventionwill become apparent from the following detailed description of theinvention when considered in conjunction with the accompanying drawingsfor example.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows an overall view of a the heat exchanger in accordance withan embodiment of the present invention,

FIG. 2 shows the heat exchanger according to the embodiment in FIG. 1 ina partially cut away illustration and partially exploded illustration,

FIG. 3 shows a cross-sectional illustration of the header according tothe version in FIG. 2,

FIG. 4 shows an alternative embodiment of the heat exchanger in apartially cut away illustration and partially exploded illustration,

FIG. 5 shows a cross-sectional illustration of the header according tothe embodiment in FIG. 4.

DETAILED DESCRIPTION

FIG. 1 shows a heat exchanger which is designed as an air conditioningcondenser 10 which is integrated into a coolant or refrigerant cycle,not illustrated, of a conventional air conditioning system of a motorvehicle.

The cooling or refrigerating fluid is supplied in gas form in the airconditioning condenser 10 and is condensed into its liquid phase, withheat being discharged. For this purpose the air conditioning condenser10 has a core region 12 with a multiplicity of tubes which are arrangedhorizontally and in parallel and over the large overall surface of whichthe heat released during the condensing or cooling of the fluid can bedischarged into the ambient air flowing around the tubes.

The air conditioning condenser 10 has, in addition to the core region 12of the individual tubes, two collecting containers 14, 16 which arearranged in each case on the end faces of the individual tubes of thecore region 12 and which are connected to the tubes. The cooling orrefrigerating fluid is supplied to and discharged from the airconditioning condenser 10 via the block screw connection 18. For thispurpose, the block screw connection 18 has a first junction 20 for thesupply and a second junction 21 for the discharge of the fluid. Thejunctions for the supplies and discharges may also be interchanged as afunction of the flow routing of the fluid.

The individual tubes of the core region 12 are connected on the endfaces to orifices on the collecting containers 14, 16, so that the fluidcirculating in the air conditioning condenser can be conducted via thecollecting containers from one individual tube to the next individualtube.

In the conventional design, the air conditioning condenser 10 has,furthermore, a filling valve 22 and a drier bottle 24 for drying thecirculating fluid by means of granulate contained in the drier bottle.Furthermore, the drier bottle 24 forms a buffer in the case of possibleoverfilling.

The block screw connection 18 may be arranged on the collectingcontainer 16, in which case the routing of the fluid may take place viathe collecting container 16 in the way outlined below, so that, apartfrom the block screw connection 18, there is no need for any furtherpipework with the corresponding additional components.

With the exception of the necessary junctions (20, 21) for the supplyand discharge of the block screw connection 18, no further componentsare necessary for the functioning and for the fastening of the airconditioning condenser 10. By virtue of this compact type ofconstruction of the air conditioning condenser 10, the latter can beheld, for example, by the collecting containers 14, 16 being pushed intocorrespondingly designed rails, for example on the cooling module.

FIG. 2 shows the collecting container 16 in a partially explodedillustration. The collecting container 16 is designed as a double tubewith the separate regions 16 a and 16 b, partitions 26 a to 26 e beingarranged transversely to the longitudinal direction of the collectingcontainer 16 and parallel to the tubes of the core region 12 in additionto the separation in the longitudinal direction of the collectingcontainer 16.

The longitudinal division of the collecting container 16 and thepartitions 26 serve for routing the fluid stream of the coolant orrefrigerant in a meandering manner through the tube system in the coreregion 12 of the air conditioning condenser 10. Slots 28 are shown inthe part region 16 a of the collecting container 16, each slot beingconnected to a tube of the core region 12.

By means of the partitions 26 a to 26 d, the individual tubes issuing ineach case between two partitions into the region 16 a of the collectingcontainer form a tube bundle in which the fluid in each case flowscodirectionally. The part region 16 a of the collecting container 16deflects the fluid stream coming from one tube bundle into the tubebundle following in series, so that the fluid stream flows through thesuccessive tube bundles in each case in the opposite direction. Thecorresponding region, not illustrated, of the second collectingcontainer 14 is constructed in a similar way to the part region 16 a ofthe collecting container and with the same function.

The fluid stream (illustrated by broken lines) enters the airconditioning condenser 10 via the supply line 20 of the block screwconnection 18. The fluid stream is conducted through a passage orifice30, provided in the partition between the region 16 a and 16 b of thecollecting container 16, into the region 16 b of the collectingcontainer (arrow A) and in this part region rises upward (arrow B) asfar as a second passage orifice 32 arranged at the upper end of thecollecting container 16, transition taking place back into the region 16b of the collecting container.

Via the orifices 28 a which are arranged in the portion of the partregion 16 a between the partitions 26 a and 26 b, the fluid streamenters the tubes which form a tube bundle and are connected to theorifices 28 a (arrow C).

After passing through these tubes and being deflected in the collectingcontainer 14, not shown, the fluid stream is returned in the next tubebundle to the collecting container 16 (arrow D).

The meandering throughflow through the tubes of the core region 12 takesplace in a similar way in the next tube bundles (arrow E, F).

The number of individual tubes forming a bundle can be determined by thepositioning of the partition 26 in adaption to the actual application.

After flowing through all the tube bundles provided, the fluid stream isled out of the air conditioning condenser by the discharge line 21 ofthe block screw connection 18 (arrow G).

The two part regions 16 a, 16 b of the collecting container 16 which aredesigned as double tube halves are produced separately from aluminum andare subsequently soldered. The block screw connection 18 is alsoconnected fixedly to the part region 16 a by soldering. The partitions26 a and 26 e arranged on the end faces of the collecting container 16in each case cover the entire cross section of the collecting container16, so that an emergence of fluid is prevented. The last portion of thethroughflow through the core region 12 (arrow F) is designed as asupercooling region in which the fluid which is already condensed outand is in the liquid phase experiences a lowering of temperature to atemperature below the evaporation temperature.

According to the cross section, shown in FIG. 3, of the collectingcontainer 16, the latter is composed of a part region 16 a designed asan open half shell and of a part region 16 b designed as a closed halfshell, these two part regions being connected to one another bysoldering. The part region 16 b fulfills the function of a supply lineto the core region of the air conditioning condenser, while the partregion 16 a serves for controlling and steering the fluid stream when itemerges from a tube bundle or when it subsequently re-enters the nextfollowing tube bundle. In this illustration, the partition 16 c can beseen, which is an integral part of the part region 16 b of closed designand which separates the part regions 16 a and 16 b over the entirelength of the collecting container 16, with the exception of the passageorifices 30, 32 (FIG. 2). The cross section according to FIG. 3 lies inthe lower portion of the header 16. FIG. 3 shows both the block screwconnection 18 and the partition 26 e which sealingly closes off theheader 16 on the lower end face of the latter and passes completelythrough the two part regions 16 a, 16 b.

FIG. 4 shows an air conditioning condenser, in which, by means of adifferently constructed collecting container 16, the flow of the fluidcan be varied, as compared with the first alternative described, in sucha way that the tube bundles follow one another such that the lastthroughflow tube bundle is not located on the bottom of the collectingcontainer 16, but in a position vertically above the latter. Thesupercooling region of the fluid can thereby be placed on a largelyfreely selectable tube bundle when the outside temperature conditionsmake this necessary. Details described separately with reference to FIG.4 correspond to those of the design alternatives described above.

Owing to the simple design of the air conditioning condenser with thetwo collecting containers 16, 14 and with the block screw connection 18arranged on the foot side of the header 16, no changes to these arenecessary.

The changed fluid flow is possible solely as a result of a structuralchange in the part region 16 b of the collecting container 16. Accordingto the variant described here, this part region is designed as a doubletube, and the fluid stream can be routed in a crossed manner in thedouble tube without any impairments.

As illustrated in FIG. 4, the supply and outlet orifices 20, 21 of theblock screw connection are controlled conversely to the way illustratedin FIG. 2, so that the fluid stream is conducted (arrow H) via thejunction of the supply line 20 into the part region 16 a and from thereinto the lowermost tube bundle, delimited by the partitions 27 f and 27g, of the core region 12. In this embodiment, the fluid is conveyedupward in the core region and is returned again in the oppositedirection in the adjacent tube bundle (arrow I). After running throughthe tube bundle according to the arrow I, the fluid stream passesthrough a first of four passage orifices 33 a into a first duct 17 a ofthe region 16 a, designed as a double tube half, of the collectingcontainer 16 and is conveyed in this to the upper end of the header 16to the second passage orifice 33 b (arrow J).

After the passage orifice 33 b, the fluid stream passes into the regionof the part region 16 a of the header 16 between the partitions 27 a and27 b and from there into the tube bundle arranged in this region (arrowK). From this tube bundle arranged in the upper portion of the coreregion 12, the fluid stream is routed in the way stated above throughthree tube bundles arranged in series (arrows L, M and N) and thenpasses, between the two partitions 27 c, 27 d, through the third passageorifice 33 c into the second chamber 17 b of the region 16 b, designedas a double tube, of the header 16. The fluid stream is routed (arrow O)through this chamber 17 b to the lower end of the header 16 and isconducted via the fourth passage orifice 33 d from the part region 16 binto the part region 16 a and from there to the outlet orifice 21 of theblock screw connection 18.

As is evident from this application according to FIG. 4, the lastthroughflow tube bundle of the core region 12 of the air conditioningcondenser 10 is located approximately in the middle of the airconditioning condenser in this alternative embodiment (arrow N). Sincethis last pass through a tube bundle constitutes the supercooling stage,if such is incorporated, it should be ensured that this region is notexposed to any heat radiation from other assemblies of the airconditioning system or of the motor vehicle.

In a conventionally arranged air conditioning system, the charge aircooler is often adjacent to the lower region of the air conditioningcondenser, so that, in the case of a high engine power, high heatradiation occurs which makes it necessary to change the location of thesupercooling stage.

It is possible to change the location of the supercooling stage, withoutadditional structural measures, by means of the header 16 designedaccording to FIG. 4.

As can be seen from FIG. 4, furthermore, the fluid stream, by beingrouted crosswise in the chambers 17 a and 17 b, can be routed throughthe core region in such a way that the position of the supercoolingstage can be as far as possible selected freely.

FIG. 5 shows a cross section of the header 16 which again is constructedfrom two half shells 16 and 16 a which consist of aluminum and aresoldered. The region 16 a has an unchanged design, as compared with thefirst variant, and again serves, above all, for steering the fluidstream from one tube bundle to the next following tube bundle. The partregion 16 b designed as a double tube has a chamber 17 a, via which thefluid, after the first two passes through the two lower tube bundles(arrow H, I according to FIG. 4), is transported into the upper regionof the header (arrow J according to FIG. 4).

After the last pass through a tube bundle, usually the supercoolingstage, the chamber 17 b receives the fluid (arrow N according to FIG. 4)and routes the supercooled fluid into the lower region of the header 16,from where the fluid leaves the air conditioning condenser via the blockscrew connection 18.

The foregoing disclosure has been set forth merely to illustrate theinvention and is not intended to be limiting. Since modifications of thedisclosed embodiments incorporating the spirit and substance of theinvention may occur to persons skilled in the art, the invention shouldbe construed to include everything within the scope of the appendedclaims and equivalents thereof.

1-14. (canceled)
 15. A heat exchanger for a fluid, comprising: a coreregion with at least two tube bundles of tubes arranged in parallel,through which the fluid flows; collecting container headers arranged onend faces of the core region and open to end faces of the tubes, asupply for supplying the fluid into the core region; a discharge fordischarging fluid out of the core region; and wherein the headersinclude transverse partitions which delimit regions of the headersthrough which the at least two tube bundles are fluidly connected inseries, and at least one header has a longitudinal partition whichsubdivides the header into a first region open to the tubes and a secondregion which is a tube bundle bypass.
 16. The heat exchanger as claimedin claim 15, wherein a block screw connection containing the supply andthe discharge is arranged at one end of one of the headers.
 17. The heatexchanger as claimed in claim 16, wherein the longitudinal partition ofthe header has at least two passage orifices.
 18. The heat exchanger asclaimed in claim 17, wherein a connection between the second part regionof the header and a tube bundle of the core region is formed by at leastone of the passage orifices in the longitudinal partition and aconnection of the second part region to the block screw connection isformed by another of the at least two passage orifices.
 19. The heatexchanger as claimed in claim 16, wherein the block screw connection isarranged fixedly on the header.
 20. The heat exchanger as claimed inclaim 15, wherein the at least one header having a longitudinalpartition is formed from an open half shell and a closed half shell. 21.The heat exchanger as claimed in claim 15, wherein the second partregion of the at least one header having a longitudinal partition facesaway from the tubes, and is continuous over a length of the header. 22.The heat exchanger as claimed in claim 21, wherein the second partregion of the header is subdivided into at least two separate ducts forthe routing of two independent fluid streams.
 23. The heat exchanger asclaimed in claim 22, wherein the at least two ducts of the second partregion are arranged in parallel.
 24. The heat exchanger as claimed inclaim 22, wherein the second part region is formed as a closed halfshell having two chambers.
 25. The heat exchanger as claimed in claim23, wherein the second part region is formed as a closed half shellhaving two chambers.
 26. The heat exchanger as claimed in claim 15,wherein the headers are configured to be received in a correspondingguide rail for holding the heat exchanger.
 27. The heat exchanger asclaimed in claim 26, wherein the heat exchanger is an air conditioningcondenser.
 28. The heat exchanger as claimed in claim 27, wherein theair conditioning condenser has a supercooling stage.
 29. The heatexchanger as claimed in claim 26, wherein the heat exchanger is a gascooler.